M416698 五、新型說明： 【新型所屬之技術領域】 本創作係有關於一種動壓軸承，尤指一種應用氧化鍅 陶瓷材料燒結製成之動壓軸承結構設計。 【先前技術】M416698 V. New description: [New technical field] This creation is about a dynamic pressure bearing, especially a dynamic pressure bearing structure designed by sintering yttria ceramic material. [Prior Art]
如幕所知，動壓軸承與滚珠轴承的最大不同，在於它 使用油/氣膜取代傳統的鋼珠，也就是說，它在轉動的時 候並未出現金屬接觸，理論上就不會有磨損的問題，是以 動壓軸承之應用，逐漸廣泛實施於高轉速需求之處。 然現行動壓軸承之結構，如US7374342B2所揭示之 hydrodynamic fluid film bearing and bearing housing with cooling capacity，其於轉軸高速運轉之啟動初期，因該氣 膜尚未形成，所以仍會有彈性壓板與轉軸產生短暫的相互 磨擦現象，而該彈性壓板與轉軸皆為金屬材質製成，故當 轉軸頻繁重覆啟動運轉時’此—彈性壓抵與高速磨擦現象 將會導致軸承發生失穩的情 Θ障况’甚至發生彈性壓板與轉軸 金屬熱融黏結之虞。 有鑑於此，本創作人基於/ 計尚有改善之必要，於是接^現行動壓軸承的彈性壓板設 動壓軸承在不有失穩的條件下本創作「動壓轴承」’期使 極佳的耐磨特性，且令壓核 於靜態啟動之時，可具有 精準，間隙不有異變之狀况生油/氣膜之間隙調教簡易 【新型内容】 種動壓軸承設計，使動壓 本創作之目的’在於提供〜 3 M416698 轴承可承受頻繁靜態啟動時，無油/氣膜磨潤之頻繁高速 摩擦狀態，而不虞有失穩、抖晃的狀況。 為達上述目的，本創作動壓軸承較佳的實施例係包含 一軸襯、一轴襯座及三個以上的壓板，用以支撐一轉軸進 行旋轉的動作，其特徵在於：該軸襯係用於與該轉軸結合 連動，其包含一結合在該轉轴的結合面，及一相反於該結 合面的第一磨擦接觸面；該轴襯座係用於套置在該轉軸， 其包含一相鄰於該軸襯第一磨擦接觸面的支持面，三個以 上凹設在該支持面的嵌槽，一個或一個以上相鄰於各該嵌 槽的定位部，及一設置在各該定位部的定位組件；及該壓 板包含有一位於一侧邊的固定端，一位於相反另一側邊的 自由端，一位在該固定端與該自由端之間的背面，一相反 該背面的第二磨擦接觸面，該固定端活動地嵌合在該軸襯 座的嵌槽，該自由端以該固定端為支點而轉動，該背面被 該定位組件頂推，致使該第二磨擦接觸面與該軸襯的第一 磨擦接觸面之間形成一可調整間距的油/氣膜間隙。 依上述較佳實施例所述之動壓軸承，其中，該軸襯包 含構成為環繞地結合在該轉軸徑向周面的一筒環，該結合 面係形成於該筒環的一内筒面並結合在該轉軸的徑向周面 0 依上述較佳實施例所述之動壓軸承，其中，該第一磨 擦接觸面係形成於該筒環相反於該結合面的一外筒面並環 繞該轉軸的徑向周面；該軸襯座貫穿的設有一套合在該筒 環的軸孔，該支持面係形成於該轴承孔的一内孔壁；該壓 M416698 板的第二磨擦接觸面係為對應該第一磨擦接觸面的凹弧面 0 依上述較佳實施例所述之動壓軸承，其中，該軸襯包 含一環繞在該外筒面的轴向擋止環，該軸向擋止環具有一 軸向擋止面，該第一磨擦接觸面係形成於該轴向擋止面； 該軸襯座貫穿的設有一套合在該轉軸的軸孔，該轴襯座相 • 鄰該第一磨擦接觸面的一端設有該支持面；該壓板的第二 … 磨擦接觸面係為對應該第一磨擦接觸面的平面。 • 依上述較佳實施例所述之動壓轴承，其中，該軸襯包 含構成為環繞地結合在該轉軸一軸向環面的一軸向擋止環 ，該軸向擋止環的一面設有該結合面，該結合面結合在該 轉軸的軸向環面，該軸向擔止環相反於該結合面的另一面 設有該第一磨擦接觸面；該軸襯座貫穿的設有一套合在該 轉軸的軸孔，該軸襯座相鄰該第一磨擦接觸面的一端設有 該支持面；該壓板的第二磨擦接觸面係為對應該第一磨擦 接觸面的平面。 ’- 依上述較佳實施例所述之動壓軸承，其中，該軸襯係 ~ - 為氧化锆陶瓷材料預先燒結製成，該結合面係緊迫結合在 該轉軸。 依上述較佳實施例所述之動壓軸承，其中，該軸襯係 為氧化鍅陶瓷材料直接喷塗成型在該轉軸再燒結製成。 依上述較佳實施例所述之動壓軸承，其中，該軸襯座 的嵌槽係為半圓槽，該壓板的固定端設有一半圓條，該半 圓條活動地嵌合在該半圓槽。 5 M416698 依上述較佳實施例所述之動壓轴承，其中，該壓板係 為氧化鍅陶瓷材料燒結製成。 依上述較佳實施例所述之動壓轴承，其中，該軸襯座 的定位部係為貫穿該軸襯座並連通到該支持面的定位孔； 該定位組件包含依序結合在該定位孔内的一調整螺絲及一 止付螺絲，該調整螺絲頂靠在該壓板的背面，該止付螺絲 頂靠在該調整螺絲。 依上述較佳實施例所述之動壓軸承，其中，該軸襯座 的定位部係為貫穿該軸襯座並連通到該支持面的定位孔； 該定位組件包含依序結合在該定位孔内的一彈性元件及一 止付螺絲，該彈性元件頂靠在該壓板的背面，該止付螺絲 頂靠在該彈性元件。 本創作之動壓軸承，透過該軸襯與轉軸連動，及各壓 板的活動結合在軸襯座的嵌槽，使各壓板的自由端受軸襯 座的定位件所限位，進而形成油/氣膜間隙，藉此克服習 知動壓軸承的問題，不虞發生失穩、抖晃及金屬熱熔黏結 的狀況，因此能達到適於高速磨擦、使轉軸穩定轉動的功 效。 【實施方式】 為使貴審查委員暸解本創作之目的、特徵及功效， 茲藉由下述具體之實施例，並配合所附之圖式，對本創作 做一詳細說明，說明如后： 參閱第一圖、第二圖及第三圖所示，本創作動壓軸承 較佳實施例的主要結構係包含一軸襯1、一軸襯座2及三 M416698 個以上壓板3，用以支撐一轉軸4進行旋轉的動作，其中 :該軸襯1係用於與轉軸4結合連動的元件，其結構包含 有一結合在轉軸4選定處的結合面11，及一相反於結合面 11的第一磨擦接觸面12，使第一磨擦接觸面12連同轉軸4 一起轉動。該軸襯座2係用於相鄰設置在該轉軸4(及軸 襯1 )的結構體，其結構包含一相鄰（對應）於軸襯1第一 磨擦接觸面12的支持面21，三個以上凹設在支持面21的嵌 槽22，一個或一個以上相鄰於各嵌槽22的定位部23，及一 設置在各定位部23的定位組件24，使定位組件24 —端突伸 於支持面21。而該壓板3的結構係包含有一位於一側邊的 固定端31，一位於相反另一侧邊的自由端32，一位在固定 端31與自由端32之間的背面33，及一相反於背面33的第二 磨擦接觸面34,其中，固定端31係活動地嵌合在軸襯座2 的嵌槽22中，使自由端32能以固定端31為支點而轉動，並 使背面33被定位組件24頂推，致使第二磨擦接觸面34與軸 襯1的第一磨擦接觸面12之間形成一可調整間距的油/氣 膜間隙A。 參閱第一圖、第二圖及第三圖所示，本創作較佳的實 施例係包含該軸襯1構成為環繞地結合在該轉轴4徑向周 面41的一筒環13，其結合面11係形成於筒環13的一内筒面 ，並透過套合或直接成型方式使結合面11結合在轉軸4的 徑向周面41。而其第一磨擦接觸面12係形成於筒環13相反 於結合面11的一外筒面，使第一磨擦接觸面12構成為環繞 轉軸4的徑向周面41的結構。另外，該軸襯座2係貫穿的 7 M416698 實施有一套合在筒環13的軸孔25，使其支持面21係形成於 轴承孔25的一内孔壁。又，參閱第三圖及第四圖所不’該 壓板3較佳的數目可為四個或八個或其他數量，而且其第 二磨擦接觸面34基於上述筒環13的實施例，係實施為對應 第一磨擦接觸面12的凹弧面，俾使背面33受定位組件22的 頂推，致使第二磨擦接觸面34與第一磨擦接觸面12之間形 成一可調整間距的油/氣膜間隙A。 本創作該軸襯1係為氧化錘陶瓷材料預先燒結製成上 述的結構，再將結合面11緊迫結合在上述轉軸4的部位， 也可以採用氧化锆陶瓷材料直接喷塗成型在轉軸4部位再 燒結製成上述的結構。 又，參閱第一圖及第三圖所示，本創作該軸襯座2的 定位部23較佳的實施例係為貫穿軸襯座2並連通到支持面 21的定位孔231;而該定位組件24較佳的實施例包含依序結 合在定位孔231内的一調整螺絲241及一止付螺絲242;藉此 使調整螺絲241端面頂靠在壓板3的背面32,透過轉動調整 螺絲241以調整第二磨擦接觸面34與第一磨擦接觸面12之 間的油/氣膜間隙A ;而止付螺絲242則係頂靠在調整螺絲 241，俾防止調整螺絲241鬆動。 本創作動壓軸承所運用的技術特徵，是以油/氣膜來 支撐結合在轉軸4的軸襯1，並提供其高速運轉所需的潤 滑，是故，該軸襯1與動壓軸承間的間隙乃極其重要。為 此，本創作係利用軸襯1與轉轴4結合，使軸襯1作為可 耐受高速磨擦的介質，而且軸襯1的第一磨擦接觸面12與 各壓板3第二磨擦接觸面34 動油/氣财成的油/的夾肖區域可域一供浮 所需的空間非常細小^隙A’此—油/氣膜間隙八 ，本創作對於此一油2供油/氣分子可通過），在此 組件2錄達成，並以=繼之調整’則是依靠定位 陏A年以. 疋位件2 4將此調整完畢的油/氣膜間 '、 疋，使油/氣臈間隙A不會異變，特別是各廢 =面33具有一剛性切，將使第一磨擦接觸= 弟擦接觸面34的油/ — 不會異變，可破保本 創作動壓轴承的油/氣膜間隙A的精準度，不虞發生失穩 抖晃及金屬熱_纟結的狀況，因此能達到適於高速磨擦 、使轉軸穩定轉動的功效。 至於本創作調整油/氣膜間隙A的步驟，係先將軸襯 1與轉軸4以校具g)定軸心位置之後，再將各組調整螺絲 241前端向壓板3的背面33抵壓，致使壓板3第二磨擦接觸 面34與軸襯1第一磨擦接觸面12形成無間隙的貼觸狀態； 其後，再依序將所有調整螺絲241均統一旋退相同的圈數， 使所有壓板3與軸襯1之間定義出一相等大小的油/氣膜 間隙A，·最後’再以止付螺絲242鎖入定位孔231，並抵靠 在調整螺絲241後端’再將固定轴襯1與轉軸4的校具移除 ’如此就能確保本創作油/氣膜間隙A的精準度。 惟依本創作的主要技術特徵而言，本創作當可再實施 應用於轉轴4的轴向方向支撲，睛參閱第五圖、第六圖及 第七圖所示，其軸向方向支撐較佳的實施例係可在該軸襯 1的筒環13外筒面環繞一軸向擋止環14，軸向擋止環14具 M416698 有至少一軸向擋止面141，如此使上述的第一磨擦接觸面 12係形成於軸向擋止面141。為此，本創作該軸襯座2改 變實施有套合在轉轴4的軸孔25，透過軸孔25將轴襯座2 套合在轉軸4，相鄰於軸向擋止環14，並在軸襯座2相鄰 (對應）第一磨擦接觸面12的一端設有上述的支持面21、嵌 槽22、定位部23及定位組件24。同時，本創作該壓板3的 數目同樣可為四個或八個或其他數量以外，其第二磨擦接 觸面34基於上述轴向擋止環14及軸向擋止面141的實施例 ，係實施為對應第一磨擦接觸面12(轴向擋止面141)的平面 ，同樣使背面33受定位組件22的頂推，致使第二磨擦接觸 面34與第一磨擦接觸面12之間形成一可調整間距的油/氣 膜間隙A。 或參閱第八圖及第九圖所示，本創作較佳的實施例包 含該軸襯1係構成為環繞地結合在轉軸4 一軸向環面42的 單一軸向擋止環15，該軸向擋止環15的一面設有上述的結 合面11，並使結合面11結合在轉軸4的軸向環面42，而軸 向擋止環15相反於結合面11的另一面則設有第一磨擦接觸 面12。為此，本創作該軸襯座2同樣可實施有套合在轉軸 4的軸孔25，透過軸孔25將軸襯座2套合在轉軸4，相鄰 於軸向擋止環14，並在軸襯座2相鄰（對應）第一磨擦接觸 面14的一端設有上述的支持面21、嵌槽22、定位部23及定 位組件24。同時，本創作該壓板3的第二磨擦接觸面34基 於上述軸向擋止環15及第一磨擦接觸面12，係實施為對應 第一磨擦接觸面12的平面，同樣使背面33受定位組件22的 10 M416698 頂推，致使第二磨擦接觸面34與第一磨擦接觸面12之間形 成可調整間距的油/氣膜間隙a。 又參閱苐一圖、第五圖或第八圖所示，本創作上述 該轴襯座2的嵌槽22較佳的實施例係為長條型的半圓槽 221 ’而該壓板3的固定端31設有一半圓條311，藉此使半 圓條311活動地嵌合在半圓槽221，即使自由端32能以固定 端31為支點而轉動。而且，該壓板3係為氧化鍅陶瓷材料 燒結製成，以形成所述的固定端31、半圓條3]^、自由端32 、背面33及第二磨擦接觸面34結構。 另外’參閱第八圖所示，本創作該定位組件24依定位 部23 (定位孔231)的數目實施有多組時，可將其中一組定位 組件24實施為依序結合在定位孔231内的一彈性元件243及 一止付螺絲242，藉此使彈性元件243頂靠在壓板3的背面 32 ’而止付螺絲242頂靠在彈性元件243。藉上述定位組件 24的彈性元件243結構設計，可提供各壓板3於轉軸4靜止 時，呈現全時彈性抵壓轴襯1的狀態，使轉軸4具有較佳 的靜壓支撐效果，而當轉軸4轉動產生油/氣膜間隙時， 各該彈性元件243則會彈性退縮，進而各壓板3仍會透過其 他的調整螺絲241而獲得剛性支撐，使所產生油/氣膜間隙 A不會異變。 雖然本創作已以上揭諸實施例來闡述，然其並非用以 限定本創作，凡任何熟悉此項技藝者，在不脫離本創作之 精神和範圍内，當可作些許等效之更動與修飾，因此本創 作之保護範圍當依後附之申請專利範圍所界定者為準。 到頻==動計，使_軸承達 義出油/氣膜的間隙，故已夂：構亦能簡易、有效的定 田介Μ 故已見功效增進無訛，且其手段運 用亦屬該_，理應合 ，惟請鈞局惠予詳審^ Μ4新型 荇審並賜准專利，實感德便。 【圖式簡單說明】 ^ 創作第—較佳實施例之立體分解示意圖。 ^ =本創作第—較佳實_之組合立體示㈣。 穿—：本創作第—較佳實補之組合剖面示意圖。 四圖為本創作第—較佳實施例之壓板數目示意圖。 圖為本創作第二較佳實施例之立體分解示意圖。 八圖為本創作第二㈣實施狀局部放大剖面示意 圖。 第七圖為本創作第二較佳實施例之應用狀態剖面示意 圖。 圖為本創作苐三較佳實施例之立體分解示意圖。 九圖為本創作第三較佳實施例之局部放大剖 面示意 圖0 M416698 【主要元件符號說明】 1 轴襯 11 結合面 12 第一磨擦接觸面 13 筒環 14 轴向擋止環 141 軸向擋止面 15 軸向擋止環 2 軸襯座 21 支持面 22 巍槽 221 半圓槽 23 定位部 231 定位孔 24 定位組件 241 調整螺絲 242 止付螺絲 243 彈性元件 25 軸孔 3 壓板 31 固定端 311 半圓條 32 自由端 33 背面 34 第二磨擦接觸面 4 轉軸 41 徑向周面 42 軸向環面 A 油/氣膜間隙 13As far as the game is concerned, the biggest difference between a dynamic pressure bearing and a ball bearing is that it uses an oil/gas film instead of a conventional steel ball. That is to say, it does not have metal contact when it is rotated, and theoretically there will be no wear. The problem is that the application of dynamic pressure bearings is gradually being widely implemented in high-speed demand. However, the structure of the action bearing, such as the hydrodynamic fluid film bearing and bearing housing with cooling capacity disclosed in US7374342B2, is still in the early stage of the high-speed operation of the rotating shaft, because the air film has not yet formed, so there will still be a short time between the elastic plate and the rotating shaft. The mutual friction phenomenon, and the elastic pressure plate and the rotating shaft are made of metal material, so when the rotating shaft frequently restarts and starts running, this - the elastic pressing and the high-speed friction phenomenon will cause the bearing to be unstable. Even the elastic plate and the shaft metal are hot-melt bonded. In view of this, the creator is still in need of improvement based on the /, so the elastic pressure plate of the current action bearing is set to the dynamic pressure bearing, and the "dynamic pressure bearing" period is excellent under the condition of no instability. The wear-resisting characteristics, and the pressure core can be accurate at the time of static start, the gap does not change, the gap between the oil and the gas film is easy to adjust. [New content] The dynamic pressure bearing design makes the dynamic pressure book The purpose of the creation is to provide ~ 3 M416698 bearings that can withstand frequent high-speed friction during oil-free/air film wear during frequent static start without any instability or jitter. In order to achieve the above object, a preferred embodiment of the dynamic pressure bearing of the present invention comprises a bushing, a bushing pedestal and three or more pressing plates for supporting a rotating shaft for rotating, wherein the bushing is used for the bushing Cooperating with the rotating shaft, comprising a bonding surface coupled to the rotating shaft, and a first frictional contact surface opposite to the bonding surface; the bushing seat is for being sleeved on the rotating shaft, and comprises a phase a support surface adjacent to the first frictional contact surface of the bushing, three or more recessed grooves recessed in the support surface, one or more positioning portions adjacent to the respective recessed grooves, and one disposed at each of the positioning portions Positioning assembly; and the pressure plate includes a fixed end on one side, a free end on the opposite side, a back between the fixed end and the free end, and a second opposite the back a frictional contact surface, the fixed end is movably fitted to the slot of the bushing seat, and the free end is rotated by the fixed end as a fulcrum, and the back surface is pushed by the positioning component, so that the second friction contact surface and the First frictional contact surface of the bushing An oil/air film gap with an adjustable spacing is formed. The dynamic pressure bearing according to the above preferred embodiment, wherein the bushing comprises a ring formed to be circumferentially coupled to a radial peripheral surface of the rotating shaft, the bonding surface being formed on an inner cylinder surface of the ring And the dynamic pressure bearing according to the preferred embodiment described above, wherein the first friction contact surface is formed on an outer cylinder surface of the ring opposite to the joint surface and surrounds a radial peripheral surface of the rotating shaft; the bushing seat is provided with a shaft hole formed in the ring, the supporting surface is formed on an inner hole wall of the bearing hole; the second frictional contact of the pressing M416698 plate The surface is a concave curved surface corresponding to the first frictional contact surface. The dynamic pressure bearing according to the preferred embodiment described above, wherein the bushing includes an axial stop ring surrounding the outer cylindrical surface, the shaft The retaining ring has an axial stop surface formed on the axial stop surface; the bushing seat is provided with a shaft hole formed in the shaft, the bushing phase • the support surface is provided at one end adjacent to the first friction contact surface; the second... frictional connection of the pressure plate It should be based on the planar surface of the first contact surface friction. The dynamic pressure bearing according to the above preferred embodiment, wherein the bushing comprises an axial stop ring configured to be circumferentially coupled to an axial toroid of the rotating shaft, one side of the axial blocking ring The joint surface is coupled to the axial annular surface of the rotating shaft, and the axial friction ring is disposed opposite to the other surface of the joint surface; the bushing seat is provided with a set The shaft hole of the rotating shaft is disposed at an end of the bushing seat adjacent to the first frictional contact surface; the second frictional contact surface of the pressing plate is a plane corresponding to the first frictional contact surface. The dynamic pressure bearing according to the above preferred embodiment, wherein the bushing is made by pre-sintering the zirconia ceramic material, and the bonding surface is tightly coupled to the rotating shaft. The dynamic pressure bearing according to the above preferred embodiment, wherein the bushing is directly spray-molded on the rotating shaft and then sintered. The dynamic pressure bearing according to the above preferred embodiment, wherein the groove of the bushing seat is a semi-circular groove, and the fixed end of the pressure plate is provided with a semi-circular strip, and the semi-circular strip is movably fitted in the semi-circular groove. 5 M416698 The dynamic pressure bearing according to the above preferred embodiment, wherein the pressure plate is made of a sintered cerium oxide ceramic material. The dynamic pressure bearing according to the preferred embodiment, wherein the positioning portion of the bushing seat is a positioning hole penetrating the bushing seat and communicating to the supporting surface; the positioning assembly includes the positioning hole sequentially included in the positioning hole An adjusting screw and a stop screw, the adjusting screw is abutted against the back of the pressing plate, and the stopping screw is abutted against the adjusting screw. The dynamic pressure bearing according to the preferred embodiment, wherein the positioning portion of the bushing seat is a positioning hole penetrating the bushing seat and communicating to the supporting surface; the positioning assembly includes the positioning hole sequentially included in the positioning hole An elastic member and a stop screw, the elastic member abuts against the back surface of the pressure plate, and the stop screw abuts against the elastic member. The dynamic pressure bearing of the present invention is coupled with the rotating shaft through the bushing, and the movement of each pressing plate is combined with the groove of the bushing seat, so that the free end of each pressing plate is limited by the positioning member of the bushing seat, thereby forming oil/ The gas film gap overcomes the problem of the conventional dynamic pressure bearing, and the occurrence of instability, chattering, and metal hot-melt bonding is achieved, so that it is suitable for high-speed friction and stable rotation of the rotating shaft. [Embodiment] In order to make your reviewer understand the purpose, characteristics and efficacy of this creation, the following specific examples are used together with the attached drawings to give a detailed explanation of the creation, as follows: As shown in the first, second and third figures, the main structure of the preferred embodiment of the present dynamic pressure bearing comprises a bushing 1, a bushing base 2 and three M416698 or more press plates 3 for supporting a rotating shaft 4 The action of the rotation, wherein: the bushing 1 is used for the element coupled with the rotating shaft 4, the structure comprises a joint surface 11 combined at the selected portion of the rotating shaft 4, and a first friction contact surface 12 opposite to the joint surface 11 The first frictional contact surface 12 is rotated together with the rotating shaft 4. The bushing base 2 is used for a structure disposed adjacent to the rotating shaft 4 (and the bushing 1), and the structure thereof comprises a supporting surface 21 adjacent to (corresponding to) the first frictional contact surface 12 of the bushing 1, three More than one recess 22 recessed in the support surface 21, one or more positioning portions 23 adjacent to the respective recesses 22, and a positioning assembly 24 disposed on each positioning portion 23, so that the positioning assembly 24 protrudes at the end On the support surface 21. The structure of the pressure plate 3 includes a fixed end 31 on one side, a free end 32 on the opposite side, a back 33 between the fixed end 31 and the free end 32, and a reverse a second frictional contact surface 34 of the back surface 33, wherein the fixed end 31 is movably fitted in the recess 22 of the bushing base 2 such that the free end 32 can be pivoted with the fixed end 31 as a fulcrum and the back surface 33 is The positioning assembly 24 is pushed up such that an oil/film gap A of adjustable pitch is formed between the second frictional contact surface 34 and the first frictional contact surface 12 of the bushing 1. Referring to the first, second and third figures, a preferred embodiment of the present invention comprises a bushing 13 which is formed to be circumferentially coupled to the radial peripheral surface 41 of the rotating shaft 4, which The joint surface 11 is formed on an inner cylindrical surface of the ring 13 and is coupled to the radial peripheral surface 41 of the rotary shaft 4 by a fitting or direct molding. The first frictional contact surface 12 is formed on the outer cylindrical surface of the ring 13 opposite to the joint surface 11, so that the first frictional contact surface 12 is configured to surround the radial peripheral surface 41 of the rotary shaft 4. Further, the shaft lining 2 is inserted through a shaft hole 25 which is fitted to the ring 13 so that the support surface 21 is formed in an inner wall of the bearing hole 25. Moreover, referring to the third and fourth figures, the preferred number of the pressure plates 3 may be four or eight or other numbers, and the second frictional contact surface 34 is implemented based on the embodiment of the above-mentioned ring 13 In order to correspond to the concave curved surface of the first frictional contact surface 12, the back surface 33 is pushed by the positioning assembly 22, so that an oil/gas with an adjustable spacing is formed between the second frictional contact surface 34 and the first frictional contact surface 12. Membrane gap A. In the present invention, the bushing 1 is pre-sintered by the oxidized hammer ceramic material to form the above structure, and the bonding surface 11 is tightly bonded to the rotating shaft 4, or the zirconia ceramic material can be directly sprayed and formed on the rotating shaft 4 portion. Sintering is carried out to form the above structure. Moreover, referring to the first and third figures, the preferred embodiment of the positioning portion 23 of the bushing base 2 is a positioning hole 231 that penetrates the bushing seat 2 and communicates with the supporting surface 21; and the positioning The preferred embodiment of the assembly 24 includes an adjusting screw 241 and a stop screw 242 which are sequentially coupled in the positioning hole 231. The end surface of the adjusting screw 241 is abutted against the back surface 32 of the pressure plate 3, and is rotated by the adjusting screw 241. The oil/air film gap A between the second frictional contact surface 34 and the first frictional contact surface 12 is adjusted; and the stop screw 242 is placed against the adjusting screw 241 to prevent the adjusting screw 241 from loosening. The technical feature of the present dynamic pressure bearing is that the oil/air film is used to support the bushing 1 combined with the rotating shaft 4, and the lubrication required for its high speed operation is provided. Therefore, the bushing 1 and the dynamic pressure bearing are interposed. The gap is extremely important. To this end, the present invention utilizes the bushing 1 in combination with the rotating shaft 4 to make the bushing 1 as a medium capable of withstanding high-speed friction, and the first frictional contact surface 12 of the bushing 1 and the second frictional contact surface 34 of each pressure plate 3 The oil/gas-filled oil/clip area can be used for the space required for floating. The gap is very small. A' this is the oil/air film gap. This creation can be used for this oil 2 oil/gas molecule. Pass), in this component 2 recorded, and = followed by adjustment 'is dependent on positioning 陏 A years to. 疋 position 2 4 adjust the oil / film between the ', 疋, make oil / gas 臈The gap A does not change, in particular, each waste=face 33 has a rigid cut, which will make the first friction contact = the oil of the wiper contact surface 34 will not change, and the oil of the created dynamic pressure bearing can be broken/ The accuracy of the air gap A can not only occur due to the instability and shaking, but also the condition of the metal heat _ 纟 knot, so that it can achieve high-speed friction and stabilize the rotation of the shaft. As for the step of adjusting the oil/film gap A in the present creation, the bushing 1 and the rotating shaft 4 are first fixed to the shaft center position, and then the front ends of the sets of adjusting screws 241 are pressed against the back surface 33 of the pressing plate 3, The second friction contact surface 34 of the pressure plate 3 and the first friction contact surface 12 of the bushing 1 form a contact state without gaps; thereafter, all the adjustment screws 241 are sequentially rotated back by the same number of turns to make all the pressure plates 3 defines an equal size oil/film gap A between the bushing 1 and finally 'locks the retaining screw 242 into the positioning hole 231 and abuts against the rear end of the adjusting screw 241' and then fixes the bushing 1 The removal of the tool with the shaft 4 'This ensures the accuracy of the created oil/film gap A. However, according to the main technical features of the creation, the present invention can be further applied to the axial direction of the rotating shaft 4, and the eye is referred to the fifth, sixth and seventh figures, and the axial direction is supported. The preferred embodiment is such that the outer tubular surface of the collar 13 of the bushing 1 surrounds an axial stop ring 14, and the axial stop ring 14 has M416698 having at least one axial stop surface 141. The first frictional contact surface 12 is formed on the axial stop surface 141. For this reason, the shaft lining 2 of the present invention is modified to have a shaft hole 25 fitted to the rotating shaft 4, and the shaft lining 2 is fitted through the shaft hole 25 to the rotating shaft 4 adjacent to the axial blocking ring 14, and The support surface 21, the groove 22, the positioning portion 23, and the positioning assembly 24 are provided at one end of the bushing base 2 adjacent to (corresponding to) the first friction contact surface 12. At the same time, the number of the pressure plate 3 can be four or eight or other numbers, and the second friction contact surface 34 is based on the embodiment of the axial stop ring 14 and the axial stop surface 141. In order to correspond to the plane of the first friction contact surface 12 (the axial stop surface 141), the back surface 33 is also pushed by the positioning assembly 22, so that a second friction contact surface 34 and the first friction contact surface 12 form a Adjust the oil / film gap A of the gap. Or, as shown in the eighth and ninth drawings, the preferred embodiment of the present invention includes the bushing 1 being configured as a single axial stop ring 15 that is circumferentially coupled to the axial axicon 42 of the rotating shaft 4, the shaft The coupling surface 11 is provided on one surface of the stopper ring 15, and the joint surface 11 is coupled to the axial annular surface 42 of the rotating shaft 4, and the axial blocking ring 15 is opposite to the other surface of the joint surface 11 A frictional contact surface 12. For this reason, the shaft lining 2 of the present invention can also be implemented with a shaft hole 25 that is fitted over the rotating shaft 4, and the shaft lining 2 is inserted through the shaft hole 25 to the rotating shaft 4, adjacent to the axial blocking ring 14, and The support surface 21, the groove 22, the positioning portion 23, and the positioning assembly 24 are provided at one end of the bushing base 2 adjacent (corresponding) to the first friction contact surface 14. At the same time, the second friction contact surface 34 of the pressure plate 3 is based on the axial stop ring 15 and the first friction contact surface 12, and is implemented as a plane corresponding to the first friction contact surface 12, and the back surface 33 is also subjected to the positioning assembly. The 10 M416698 push of 22 causes an oil/film gap a of adjustable pitch to be formed between the second frictional contact surface 34 and the first frictional contact surface 12. Referring also to FIG. 1 , FIG. 5 or FIG. 8 , the preferred embodiment of the above-mentioned inserting groove 22 of the bushing base 2 is a long semicircular groove 221 ′ and the fixed end of the pressing plate 3 . 31 is provided with a half round bar 311, whereby the semicircular strip 311 is movably fitted in the semicircular groove 221, even if the free end 32 can be rotated with the fixed end 31 as a fulcrum. Further, the press plate 3 is made of a sintered cerium oxide ceramic material to form the fixed end 31, the semicircular strip 3, the free end 32, the back surface 33, and the second rubbing contact surface 34. In addition, as shown in the eighth figure, when the positioning assembly 24 is implemented in a plurality of groups according to the number of the positioning portions 23 (positioning holes 231), one of the positioning assemblies 24 may be implemented to be sequentially coupled in the positioning holes 231. An elastic member 243 and a stop screw 242 are used to abut the elastic member 243 against the back surface 32' of the pressure plate 3 and the stop screw 242 abuts against the elastic member 243. By the structural design of the elastic member 243 of the positioning component 24, the pressure plate 3 can be fully elastically pressed against the bushing 1 when the rotating shaft 4 is stationary, so that the rotating shaft 4 has a better static pressure supporting effect, and when the rotating shaft 4 4 When the oil/air film gap is generated by rotation, each of the elastic members 243 is elastically retracted, and the pressure plates 3 are still rigidly supported by the other adjusting screws 241, so that the generated oil/film gap A does not change. . Although the present invention has been described above by way of example, it is not intended to limit the present invention, and any person skilled in the art can make some equivalent changes and modifications without departing from the spirit and scope of the present invention. Therefore, the scope of protection of this creation is subject to the definition of the scope of the patent application attached. To frequency == motion meter, so that the _ bearing up to the oil / gas film gap, it has been said: the structure can also be simple and effective Ding Tian Jie, so it has seen the effectiveness of the improvement, and its means of application _, should be combined, but please ask the bureau for a detailed review ^ Μ 4 new trial and grant a patent, the real sense of virtue. BRIEF DESCRIPTION OF THE DRAWINGS ^ A schematic exploded perspective view of a preferred embodiment. ^ = The combination of the creation of the first - better _ stereo (4). Wear -: The schematic diagram of the combination of the first and the best. The four figures are schematic views of the number of platens in the first preferred embodiment of the present invention. The figure is a perspective exploded view of a second preferred embodiment of the present invention. Figure 8 is a partially enlarged cross-sectional schematic view of the second (four) embodiment of the creation. Figure 7 is a schematic cross-sectional view showing the application state of the second preferred embodiment of the present invention. The figure is a perspective exploded view of a preferred embodiment of the present invention. 9 is a partially enlarged cross-sectional view of the third preferred embodiment of the present invention. M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M M Face 15 Axial stop ring 2 Bushing seat 21 Support surface 22 Groove 221 Semicircular groove 23 Positioning part 231 Positioning hole 24 Positioning assembly 241 Adjustment screw 242 Stop screw 243 Elastic element 25 Shaft hole 3 Pressure plate 31 Fixed end 311 Semi-circular strip 32 Free end 33 Back 34 Second friction contact surface 4 Rotary shaft 41 Radial circumferential surface 42 Axial torus A Oil/film gap 13